JP7262087B2 - Equal reduction gear by variable linear velocity planetary gear mechanism with two sun gears - Google Patents

Description

TECHNICAL FIELD The present invention relates to the technical field of a planetary gear mechanism transmission, and more particularly, it has a variable linear velocity planetary gear mechanism with two sun gears, and the combination of the number of teeth of each gear matches the number of gear groups, which is practical. It relates to a speed reducer that can be assembled and operates evenly.

A normal planetary gear mechanism is a common structure in the mechanical field, and has three parts: a sun gear, an internal gear, and a planetary carrier. It is a normal planetary gear since only one gear is provided on the gear shaft. Different from the ordinary planetary gear mechanism, the variable linear velocity planetary gear mechanism with two sun gears according to the present invention is composed of three parts: a left sun gear, a right sun gear and a planetary carrier with planetary gears. be done. The planetary carrier has two or more planetary gear axes, and each planetary gear axis is provided with a left planetary gear and a right planetary gear in this order from the left side. A variable linear velocity planetary gear mechanism with two sun gears should be called a "double sun gear external meshing planetary gear mechanism" according to the nomenclature in the art. In this field, "a variable linear velocity planetary gear mechanism with two sun gears" is not recognized as an independent planetary gear mechanism, and such a planetary gear mechanism is a "Ferguson wonder machine" and practical assembly is impossible. It is said that they cannot operate evenly. The inventor proposes as follows. Set the number of gear groups to 2 or more, set the value range defining parameter, and apply the manufacturing and assembly rules for planetary gears with the rule that the combination of the number of teeth matches the number of gear groups, and specify the pitch circle radius of the gear. and connecting the planet carrier to the input end, one sun gear to the locking end, and the other sun gear to the output end, the variable linear velocity planetary gear mechanism with two sun gears is It is established as a speed reducer that can be practically assembled and operates evenly. If the number of sets of gears is less than 2, the operation of the planetary gear mechanism is uneven, accompanied by large vibrations during operation. If the combination of the number of teeth does not match the range defining parameters, the speed reducer will not work. For example, when the combinations of the number of teeth of the left sun gear, the right sun gear, the left planetary gear, and the right planetary gear are 60, 80, 18, and 24, the value of the range defining parameter becomes 1.0 depending on the combination of the numbers of teeth. Therefore, the variable linear velocity planetary gear mechanism with two sun gears cannot perform reduction transmission. If the combination of the number of teeth does not match the number of sets of gears, the sun gear variable linear velocity planetary gear mechanism cannot be practically assembled. For example, if the combinations of the number of teeth of the left sun gear, the right sun gear, the left planetary gear, and the right planetary gear are 99, 100, 100, and 101, and the number of gear sets is 2, the combination of the number of teeth is A variable linear velocity planetary gear mechanism with two such sun gears, which does not match the number of sets, cannot be practically assembled. In this field, it is considered that a variable linear velocity planetary gear mechanism with two sun gears cannot be practically assembled because it does not conform to the manufacturing and assembly rules for planetary gears and does not conform to the pitch circle radius regulations of gears. .

The object of the present invention is to use a variable linear velocity planetary gear mechanism with two sun gears, set the number of gear groups to two or more, set a range defining parameter, and match the number of teeth to the number of gear groups. Based on this rule, the combination of the number of teeth and the number of sets of gears are set, the manufacturing and assembly rules for planetary gears are applied, the pitch circle radius of gears is applied, and the three parts, input end, output end, and lock end, are applied. and to construct a speed reducer that can be practically assembled and operates uniformly.

A uniform reducer by a variable linear velocity planetary gear mechanism with two sun gears comprises a variable linear velocity planetary gear mechanism with two sun gears, an input end, an output end, a lock end, and an auxiliary such as a bearing. device.

A variable linear velocity planetary gear mechanism with two sun gears is composed of three parts: a left sun gear, a right sun gear, and a planetary carrier with planetary gears. The left sun gear and the right sun gear are positioned inward in this order from the left side, the sun gear is a gear, and the two sun gears have different pitch circle radii. A planetary carrier with planetary gears is located outside, the planetary carrier supports each planetary gear by bearings on the planetary carrier, each planetary gear is the same, and the number of planetary gear axes supported by the planetary carrier is equal to the gear is the number of sets K of . The three parts have a common axis of rotation called the axis of revolution, with each planetary gear axis evenly spaced around the revolution axis, each planetary gear axis parallel to the orbital axis, and each planetary gear axis are equal to the axis of revolution, and this distance is the reference center distance. Each planetary gear is provided with two gears, a left planetary gear and a right planetary gear, in the order from left to right on its axis, and each pair of left planetary gear and right planetary gear is connected to each other, and the left planetary gear and right planetary gear are connected to each other. have the same number of revolutions but different pitch circle radii. The left planetary gear meshes with the left sun gear, the right planetary gear meshes with the right sun gear, and the two sun gears do not connect or mesh with each other. A bearing is provided to allow the three parts to rotate relative to each other, so that each planetary gear follows the planetary carrier to revolve around its revolution axis and rotate around its planetary gear axis, and the three parts are prevented from sliding relative to each other along the direction of the axis of revolution, and the planetary gear and the planetary carrier are prevented from sliding relative to each other along the direction parallel to the axis of revolution. The left planetary gear and the right planetary gear have different pitch linear velocities, the left sun gear and the right sun gear have different pitch linear velocities, and the same planetary gear mechanism has two pitch linear velocities. planetary gear mechanism”. There are two methods for the planetary carrier to support each planetary gear. Method 1 is to use the planetary gear as a shaft and the planetary carrier as a bearing, as shown in FIGS. Method 2 uses a planetary carrier as an axis and a planetary gear as a bearing, as shown in FIGS. The two ways that the planetary carrier supports each planetary gear have the same technical effect, and under the condition that other structures are the same, the transmission ratio of the speed reducer is exactly the same. The combination of the number of teeth is a set of the number of teeth of the left sun gear, the number of teeth of the right sun gear, the number of teeth of the left planetary gear, the number of teeth of the right planetary gear, and the number of teeth of these four gears. "Number of teeth of right sun gear*Number of teeth of left planetary gear/(Number of teeth of left sun gear*Number of teeth of right planetary gear)" is the value range defining parameter of the present invention.

As for the range defining parameter, the value of the range defining parameter is greater than 0.875, less than 1.142857, and not 1.0 for each combination of numbers of teeth.

The gear set number K of the variable linear velocity planetary gear mechanism having two sun gears is an integer of 2 or more, and when setting the number of teeth and the number of gear sets, the combination of the number of teeth is the number of gear sets. The rules to match are: When the absolute value of the difference between the number of teeth of the left sun gear and the number of teeth of the right sun gear is a multiple of 2, the number of gear sets shall be 2, and the difference between the number of teeth of the left sun gear and the number of teeth of the right sun gear When the absolute value of is a multiple of 3, the number of gear groups shall be 3, and when the absolute value of the difference between the number of teeth of the left sun gear and the number of teeth of the right sun gear is a multiple of 4, the number of gear groups is either 4 or 2, and when the absolute value of the difference between the number of teeth of the left sun gear and the number of teeth of the right sun gear is a multiple of 5, the number of gear sets is 5, and the number of teeth of the left sun gear When the absolute value of the difference between the number of teeth of the right sun gear and the number of teeth of the right sun gear is a multiple of 6, the number of sets of gears shall be either 6, 3, or 2, and the number of teeth of the left sun gear and the number of teeth of the right sun gear shall be When the absolute value of the difference is a multiple of 8, the number of gear sets shall be 8, 4, or 2, and the absolute value of the difference between the number of teeth of the left sun gear and the number of teeth of the right sun gear shall be a multiple of 10. , the number of sets of gears is either 5 or 2. The number of gear sets should not be too large to avoid neighboring planetary gears colliding with each other.

A planetary gear mechanism with two sun gears is provided with a section perpendicular to the axis of revolution and in contact with each of the left planetary gears, which is called the left section. At a certain distance, another section perpendicular to the axis of revolution and tangential to each of the right planetary gears is provided, referred to as the right section. In the left cross section and right cross section, in the edge curve of one tooth cross section of the planetary gear, from the midpoint of the root to the midpoint of the next root is called a complete tooth, and the shape of the edge curve of the cross section of the tooth is sine. Regardless of whether it is curved or not, the phase angle value of the root midpoint is 0, the phase angle value of the tip midpoint of the tooth is π, and the phase of the next root midpoint is The angular value is 2π. Thus, with the pitch arc as the abscissa axis, each point on the edge curve of the tooth cross-section has a corresponding abscissa value, or phase angle value. This method of giving a phase angle value to each point on the edge curve of the tooth cross section is commonly used in the motor field and will be understood in the mechanical field. Please refer to FIG. The midpoint of the next tooth bottom is the point where the phase angle value of the tooth is 2π, and the point where the phase angle value of the adjacent previous tooth is 4π, and the phase angle value of the next adjacent tooth is 0. It is also a point. Each planetary gear of a variable linear velocity planetary gear mechanism with two sun gears is provided with a radial section that contacts both the left section and the right section, which gives the phase angle value of the left planetary gear tooth and the value of the right planetary gear tooth. There always exists a radial section with the same phase angle value, the radial section is an equiphase surface, and the intersection of the equiphase surface and the edge curve of the tooth section in the left section is the left equiphase point. The intersection of the surface and the edge curve of the tooth section in the right section is the right equiphase point, the left equiphase point, the phase angle value of the right equiphase point is the equiphase angle value a, and the value of a The range is 0 to 2π. In the present invention each planetary gear has at least one equiphase surface. When the number of teeth of the left planetary gear and the number of teeth of the right planetary gear are equal, the planetary gear has an infinite number of equiphase surfaces. In a variable linear velocity planetary gear mechanism having two sun gears, the number of sets of gears K is set, and the plane to which the first planetary gear axis and the revolution axis belong in the clockwise direction is the first mounting surface, The plane to which the second planetary gear axis and the revolution axis belong is the second mounting surface, the plane to which the third planetary gear axis and the revolution axis belong is the third mounting surface, and thus the fourth mounting surface. , the fifth mounting surface, the sixth mounting surface, the seventh mounting surface, and finally the Kth mounting surface as the plane to which the Kth planetary gear axis and revolution axis belong. The included angle between adjacent mounting surfaces is (360 degrees/K). The number of teeth of the left sun gear is divided by the number of gear sets K to obtain a remainder, and the remainder value ranges from 0 to (K-1) and is an integer. The difference between equiphase angle values of adjacent planetary gears is (2π*remainder value/K).

The manufacturing and assembly rules for planetary gears are as follows. When manufacturing each planetary gear, for the first planetary gear, the equiphase surface is selected so that the equiphase angle value is a, where a is generally 0, and for the second planetary gear, selects an equiphase surface such that the equiphase angle value is (a+1*2π*modulus value/K), and for the third planetary gear, the equiphase angle value is (a+2*2π*modulus value/ K), and thus manufacturing the 4th planetary gear, the 5th planetary gear, the 6th planetary gear, the 7th planetary gear in sequence, Finally, in the K-th planetary gear, an equiphase surface is selected so that the equiphase angle value is (a+(K−1)*2π*remainder/K). When assembling each planetary gear, two sun gears and planetary carriers are assembled at predetermined positions on the revolution axis, each mounting surface is determined, and the equiphase angle value of the first planetary gear is a. The surface is superimposed on the first mounting surface, the left and right equiphase points are set within the reference center distance, the first planetary gear is assembled, and the equiphase angle value of the second planetary gear is (a+1*2π* The equiphase surface that is the remainder value /K) is superimposed on the second mounting surface, the left and right equiphase points are set within the reference center distance, the second planetary gear is assembled, and the third planetary gear etc. The equiphase surface whose phase angle value is (a+2*2π*remainder/K) is superimposed on the third mounting surface, and the left and right equiphase points are set within the reference center distance to assemble the third planetary gear. , in this way, the fourth planetary gear, the fifth planetary gear, the sixth planetary gear, and the seventh planetary gear are sequentially assembled, and finally the equiphase angle of the Kth planetary gear is An equiphase surface whose value is (a+(K−1)*2π*remainder value/K) is superimposed on the Kth mounting surface, and the left and right equiphase points are set within the reference center distance, and the Kth planetary gear Assemble the

The regulations for the pitch circle radius of gears are as follows. The number of teeth of the left sun gear/the number of teeth of the left planetary gear = the pitch circle radius of the left sun gear/the pitch circle radius of the left planetary gear, and the pitch circle radius of the left sun gear + the pitch circle radius of the left planetary gear = the reference center Set the pitch radius of the left sun gear and the pitch radius of the left planetary gear to be the distance. The number of teeth of the right sun gear/the number of teeth of the right planetary gear = the pitch circle radius of the right sun gear/the pitch circle radius of the right planetary gear, and the pitch circle radius of the right sun gear + the pitch circle radius of the right planetary gear = the reference Set the pitch radius of the right sun gear and the pitch radius of the right planetary gear to be the center distance. The left sun gear, each left planetary gear, the right sun gear, each right planetary gear should all meet this regulation. As is well known in this field, the reference center distance and pitch circle radius of the gear are actually allowed to deviate within a certain range.

There are two ways to connect the three parts of the variable linear velocity planetary gear mechanism with two sun gears, the input end, the output end and the lock end. different. As connection method 1, the planet carrier is connected to the input end, the left sun gear is connected to the output end, the right sun gear is connected to the lock end, and the transmission ratio of the transmission from the planet carrier to the left sun gear is the left transmission ratio and the left transmission ratio=1/(1−number of teeth of right sun gear*number of teeth of left planetary gear/(number of teeth of left sun gear*number of teeth of right planetary gear)). As connection method 2, the planet carrier is connected to the input end, the right sun gear is connected to the output end, the left sun gear is connected to the lock end, and the transmission ratio of the transmission from the planet carrier to the right sun gear is the right transmission ratio and the right transmission ratio=1/(1−number of teeth of left sun gear*number of teeth of right planetary gear/(number of teeth of right sun gear*number of teeth of left planetary gear)). As a result, it can be seen that the right transmission ratio = the reciprocal of the left transmission ratio + 1.0. 1 and 2 for connection method 1, and FIGS. 3 and 4 for connection method 2. FIG. When the transmission ratio value is positive, the direction of the rotation speed of the input end and the rotation speed of the output end is the same; when the value of the transmission ratio is negative, the rotation speed of the input end and the rotation speed of the output end The direction of the numbers is reversed. The input end is connected to the power device to input power. The output end is connected to a power using device to output power. The lock end is connected to a zero rotation speed device such as a speed reducer housing, and the rotation speed of the lock end is zero. Keeping the lock end connection as it is, if the part connected to the input end and the part connected to the output end are exchanged, the reducer becomes an accelerator, and the transmission ratio of the accelerator is the reciprocal of the transmission ratio of the corresponding reducer. . Said connection is the connection of two objects via a mechanical connection device, so that the rotational speeds of the two objects are exactly the same. “*” is the multiplication sign, “/” is the division sign, “=” is the equal sign, “-” is the subtraction sign, “+” is the addition sign, and “π” is the pi sign, which indicates the phase angle. show.

The fact that the number of sets of gears is two or more is a condition for the speed reducer of the present invention to operate uniformly. The rule that the combination of the number of teeth of the variable linear velocity planetary gear mechanism with two sun gears matches the number of gear sets has never been proposed in this field, and the present invention proposes it for the first time. A range defining parameter is a requirement of the present invention. In this field, there are general conditions for assembling planetary gears of a planetary gear mechanism, but the format and contents thereof are completely different from the "manufacturing and assembling rules for planetary gears" described in the present invention. For the first time, we have proposed manufacturing and assembling rules (rules) for planetary gears in a variable linear velocity planetary gear mechanism. In this field, there is a method of setting the pitch circle radius of a pair of two normal gears around the reference center distance, but the present invention is the left sun gear, the left planetary gear, the right sun gear, and the right planetary gear around the same reference center distance. It is the first time to propose a method of setting the pitch radii of two pairs of four gears at the same time, that is, to define the pitch radii of gears.

The auxiliary devices such as bearings are conventional techniques in the mechanical field, and the supporting effect of the bearings must meet the requirements of the present invention. Gears according to the present invention include various forms of gears such as cylindrical gears, arc gears, spur gears, and helical gears (bevel gears). The core characteristics of the reducer are the transmission ratio and the even action. The core characteristic of the variable linear velocity planetary gear mechanism with two sun gears is that it can be assembled practically. The actual assembly is determined according to the planetary gear manufacturing and assembly rules and the regulation of the pitch circle radius of the gear. Parameters such as the material of each part and device of the reducer, the length of the reference center distance of the reducer, the tooth depth, tooth width, and shift coefficient of the gear, as well as the mechanical properties, durability, etc. It depends on the actual characteristics, which is a matter that can be solved by ordinary knowledge in this field, and has nothing to do with the transmission ratio and the actual assembly, so no specific description is given in this specification.

Beneficial effects of the present invention are as follows. Using a variable linear velocity planetary gear mechanism with two sun gears, the number of sets of two or more gears, the value range defining parameter, the rule that the combination of the number of teeth matches the number of sets of gears, and the rules for manufacturing and assembling planetary gears. , Proposing the definition of the gear pitch radius, connecting the planetary carrier to the input end, connecting one sun gear to the locking end, and connecting the other sun gear to the output end, a practical assembly is possible. proposed to construct a speed reducer that operates in equilibrium with Conventional reduction gears are mainly gear reduction gears, normal planetary gear reduction gears, strain wave gear reduction gears, and cycloidal reduction gears. A gear reducer, usually a reducer based on a planetary gear mechanism, has a small transmission ratio value, and requires a complicated serial multi-stage reduction to obtain a large transmission ratio value. Strain wave gear reducers and cycloidal reducers have a higher transmission ratio value, but are not suitable for high power transmission due to their complicated structure and high cost. The speed reducer of the present invention has a low level of gear meshing from the input end to the output end during transmission, low loss, simple structure, low cost, high transmission efficiency, large transmission ratio value range, and small power transmission. It is also suitable for high power transmission and can replace the traditional speed reducer.

FIG. 1 is a structural schematic diagram of an equal reduction gear with a variable linear velocity planetary gear mechanism having two sun gears of the present invention, in which a left sun gear is connected to an output end and a planetary carrier serves as a bearing. FIG. 2 is a structural schematic diagram of an equal reduction gear by a variable linear velocity planetary gear mechanism having two sun gears according to the present invention, in which the left sun gear is connected to the output end and the planetary carrier is the axis. FIG. 3 is a structural schematic diagram of an equal reduction gear with a variable linear velocity planetary gear mechanism having two sun gears of the present invention, in which the right sun gear is connected to the output end and the planetary carrier serves as a bearing. FIG. 4 is a structural schematic diagram of an equal reduction gear with a variable linear velocity planetary gear mechanism having two sun gears of the present invention, in which the right sun gear is connected to the output end and the planetary carrier is the axis. FIG. 5 is a structural schematic diagram of an equal reduction gear using a variable linear velocity planetary gear mechanism having two sun gears according to Embodiment 1 of the present invention. In the figure, 8 is a locking end that forms a variable connection with the right sun gear and is symbolized as a disc brake with the brake caliper grounded. FIG. 6 is a schematic diagram of an equiphase surface in which the left cross section and the right cross section of the planetary gear overlap. 1 is the corresponding bottom midpoint of the left gear, 2 is the top midpoint of the left gear, 3 is the next bottom midpoint of the left gear, 4 is the corresponding bottom midpoint of the right gear, 5 is the right gear tooth The pre-midpoint, 6, is the next root midpoint of the right gear, and 7 is the radial section, or equiphase surface.

1 to 5, 1 is the left sun gear, 2 is the right sun gear, 3 is the planetary carrier, 4 is the left planetary gear, 5 is the right planetary gear, 6 is the input end, 7 is the output end, 8 is the lock end.

1 to 5, each planetary gear mechanism is shown as a schematic diagram of half of the whole based on common recognition in this field, and connections and structural relationships are shown for each part, The actual dimensions are not reflected, auxiliary devices such as bearings, bearings, and housings are omitted, the input arrow schematically indicates the input end, the output arrow schematically indicates the output end, and the ground The symbol schematically indicates the lock end at zero rotation speed.

(Example 1)
A uniform reduction gear by a variable linear velocity planetary gear mechanism having two sun gears includes a variable linear velocity planetary gear mechanism having two sun gears, an input end 6, an output end 7, a lock end 8, bearings, etc. Ancillary equipment. As shown in FIG. 5, ancillary devices such as bearings are not drawn in the figure, and the locking end is shown as a disc brake with the brake caliper grounded.

A variable linear velocity planetary gear mechanism with two sun gears is composed of three parts: a left sun gear 1, a right sun gear 2, and a planetary carrier 3 with planetary gears. The left sun gear 1 and the right sun gear 2 are positioned on the outer side in order from left to right, and the two sun gears have different pitch circle radii. A planetary carrier 3 with planetary gears is located inside, the planetary carrier 3 supports each planetary gear, each planetary gear being identical. The three parts have a common axis of rotation called the axis of revolution, with each planetary gear axis evenly spaced around the revolution axis, each planetary gear axis parallel to the orbital axis, and each planetary gear axis are equal to the axis of revolution, and this distance is the reference center distance. Each planetary gear is provided with two gears, a left planetary gear 4 and a right planetary gear 5, in left and right order on its axis, and each pair of left planetary gear 4 and right planetary gear 5 are connected to each other. and the right planetary gear 5 have the same rotational speed but different pitch circle radii. The left planetary gear 4 meshes with the left sun gear 1, the right planetary gear 5 meshes with the right sun gear 2, and the two sun gears do not connect or mesh with each other. Bearings are provided to allow the three parts to rotate relative to each other, so that each planetary gear can follow the planetary carrier 3 to revolve around its revolution axis and rotate around its planetary gear axis, The parts are prevented from sliding relative to each other along the direction of the axis of revolution, and the planetary gear and planet carrier 3 are prevented from sliding relative to each other along the direction parallel to the axis of revolution. There are two methods for the planetary carrier 3 to support each planetary gear. In this embodiment, the planetary gear is used as a shaft and the planetary carrier 3 is used as a bearing.

The combination of tooth numbers in this example results in a range defining parameter value of 357/361, which is approximately 0.9889196676, meeting the range defining parameter requirements.

In this embodiment, the number of teeth of the left sun gear is 38, the number of teeth of the right sun gear is 42, the number of teeth of the left planetary gear is 17, and the number of teeth of the right planetary gear is 19. is 4 and matches the rule that the combination of the number of teeth matches the number of sets of gears. Since the number of sets of gears is not large, adjacent planetary gears do not collide with each other.

In this embodiment, manufacturing and assembly rules for planetary gears are applied. The remainder value is two in this example. When manufacturing each planetary gear, for the first planetary gear, the equiphase surface is selected to have an equiphase angle value of 0, and for the second planetary gear, an equiphase angle value of π , for the third planetary gear select an equiphase surface such that the equiphase angle value is 0, and for the fourth planetary gear select an equiphase angle value Choose an equiphase surface such that is π. When assembling each planetary gear, the two sun gears and the planetary carrier 3 are assembled at a predetermined position on the revolution axis, each mounting surface is fixed, and the equiphase angle value of the first planetary gear is 0, etc. The phase surface is superimposed on the first mounting surface, the left and right equiphase points are set within the reference center distance, the first planetary gear is assembled, and the equiphase angle value of the second planetary gear is π, etc. The phase surface is superimposed on the second mounting surface, the left and right equiphase points are set within the reference center distance, the second planetary gear is assembled, and the equiphase angle value of the third planetary gear is 0, etc. The phase surface is superimposed on the third mounting surface, the left and right equiphase points are set within the reference center distance, the third planetary gear is assembled, and the equiphase angle value of the fourth planetary gear is π, etc. The phase surface is superimposed on the fourth mounting surface, the left and right equiphase points are set within the reference center distance, and the fourth planetary gear is assembled.

In this embodiment, the reference center distance is 200 mm, the pitch radius of the left sun gear is 138.1818182 mm, the pitch radius of the left planetary gear is 61.8181818 mm, and the pitch radius of the right sun gear is 137.704918 mm. and the pitch circle radius of the right planetary gear is 62.295082 mm. Conforms to the gear pitch circle radius regulations.

This embodiment uses the connection method 1 to configure the speed reducer, the planetary carrier 3 is connected to the input end 6, the left sun gear 1 is connected to the output end 7, and the right sun gear 2 is connected to the lock end 8. , the transmission ratio of the transmission from the planetary carrier 3 to the left sun gear 1 is the left transmission ratio, and the left transmission ratio = 1/(1 - the number of teeth of the right sun gear * the number of teeth of the left planetary gear / (the number of teeth of the left sun gear The number of teeth*the number of teeth of the right planetary gear))=90.25. The input end 6 is connected to a power device, namely an engine, to input power. The output end 7 is connected to the power using device, namely the main rotor, to output power. The right sun gear 2 is connected to the lock end 8 via a mechanical connection, ie a disc brake, which is not a constant connection but a variable connection. The disc brake is a conventional product in the field, with the brake disc connected to the right sun gear 2 and the brake caliper connected to the locking end 8 . When the brake caliper engages the brake disc, the rotation speed of the right sun gear 2 is zero, the power input from the input end 6 is completely transmitted to the output end 7, and the brake caliper releases the brake disc. , the right sun gear 2 becomes free. When the right sun gear 2 is free, the resistance is very small, and when there is resistance at the output end 7, the power input from the input end 6 is transmitted to the right sun gear 2, causing it to idle, and the output end 7 obtains power. I can't. Therefore, the speed reducer of this embodiment can be used for the transmission of the main rotor of a helicopter, and since the right sun gear 2 and the lock end 8 are variably connected, the speed reducer functions as a clutch. Auxiliary devices such as bearings use conventional techniques in the mechanical field, and the support effect of the bearings must meet the requirements of this embodiment.

The relationship of motion during operation of the speed reducer of this embodiment is that the rotational direction of the planetary carrier 3 and the rotational direction of the left sun gear 1 are the same.

The total transmission ratio of the main rotor of a helicopter is around 80 to 100, and in order to obtain such a total transmission ratio in the conventional main rotor transmission, a two-stage planetary gear mechanism as the main reducer and a bevel gear reducer are generally used. In addition, it is necessary to use a three-stage series reduction, and in the main reduction gear, there are four levels of gear meshing from the input end to the output end. It is low, and it is necessary to provide a separate clutch for the transmission of the main rotor. The speed reducer of this embodiment has only two levels of gear meshing from the input end to the output end, so the loss is small, the structure is simple, the cost is low, the transmission efficiency is high, and there is no need to provide a separate clutch. , the speed reducer of this embodiment can be used for the transmission of the main rotor of the helicopter instead of the conventional speed reducer.

(Example 2)
A uniform reduction gear by a variable linear velocity planetary gear mechanism having two sun gears includes a variable linear velocity planetary gear mechanism having two sun gears, an input end 6, an output end 7, a lock end 8, bearings, etc. Ancillary equipment. Referring to FIG. 1, ancillary equipment such as bearings are not drawn in the figure.

The configuration and structure of the variable linear velocity planetary gear mechanism having two sun gears are the same as those of the first embodiment. There are two methods for supporting the planetary gears by the planetary carrier 3. Method 1 is used in this embodiment. As shown in FIG. When using Method 2, as shown in FIG. 2, the planetary gear is the bearing and the planetary carrier is the axis. The two ways in which the planetary carrier 3 supports each planetary gear have the same technical effect.

The combination of the number of teeth in this example results in a range defining parameter value of 220/221, which is approximately 0.9954751131, meeting the range defining parameter requirements.

In this embodiment, the number of teeth of the left sun gear is 26, the number of teeth of the right sun gear is 22, the number of teeth of the left planetary gear is 20, and the number of teeth of the right planetary gear is 17. is 4 and matches the rule that the combination of the number of teeth matches the number of sets of gears. Since the number of sets of gears is not large, adjacent planetary gears do not collide with each other.

In this embodiment, manufacturing and assembly rules for planetary gears are applied. The remainder value is two in this example. When manufacturing each planetary gear, for the first planetary gear, the equiphase surface is selected to have an equiphase angle value of 0, and for the second planetary gear, an equiphase angle value of π , for the third planetary gear select an equiphase surface such that the equiphase angle value is 0, and for the fourth planetary gear select an equiphase angle value Choose an equiphase surface such that is π. When assembling each planetary gear, the two sun gears and the planetary carrier 3 are assembled at a predetermined position on the revolution axis, each mounting surface is fixed, and the equiphase angle value of the first planetary gear is 0, etc. The phase surface is superimposed on the first mounting surface, the left and right equiphase points are set within the reference center distance, the first planetary gear is assembled, and the equiphase angle value of the second planetary gear is π, etc. The phase surface is superimposed on the second mounting surface, the left and right equiphase points are set within the reference center distance, the second planetary gear is assembled, and the equiphase angle value of the third planetary gear is 0, etc. The phase surface is superimposed on the third mounting surface, the left and right equiphase points are set within the reference center distance, the third planetary gear is assembled, and the equiphase angle value of the fourth planetary gear is π, etc. The phase surface is superimposed on the fourth mounting surface, the left and right equiphase points are set within the reference center distance, and the fourth planetary gear is assembled.

In this embodiment, the reference center distance is 30 mm, the pitch radius of the left sun gear is 16.96562174 mm, the pitch radius of the left planetary gear is 13.03437826 mm, and the pitch radius of the right sun gear is 16.92307692 mm. and the pitch circle radius of the right planetary gear is 13.07692308 mm. Conforms to the gear pitch circle radius regulations.

This embodiment uses the connection method 1 to configure the speed reducer, the planetary carrier 3 is connected to the input end 6, the left sun gear 1 is connected to the output end 7, and the right sun gear 2 is connected to the lock end 8. , the transmission ratio of the transmission from the planetary carrier 3 to the left sun gear 1 is the left transmission ratio, and the left transmission ratio = 1/(1 - the number of teeth of the right sun gear * the number of teeth of the left planetary gear / (the number of teeth of the left sun gear The number of teeth*the number of teeth of the right planetary gear))=221. The input end 6 is connected to a power device to input power. The output end 7 is connected to a power using device to output power. The lock end 8 is connected to the speed reducer housing, and the rotation speed of the lock end 8 is zero. Auxiliary devices such as bearings use conventional techniques in the mechanical field, and the support effect of the bearings must meet the requirements of this embodiment.

The relationship of motion during operation of the speed reducer of this embodiment is that the rotational direction of the planetary carrier 3 and the rotational direction of the left sun gear 1 are the same.

The transmission ratio value is about 220, which is the transmission ratio value used for the speed reducer of the robot joint attached to the high speed motor. Conventional robot joint reduction gears are mainly cycloidal reduction gears, namely RV reduction gears. Although the RV reduction gears can achieve such a transmission ratio value, they are complicated in structure and high in cost. The speed reducer of this embodiment has a simple structure, is inexpensive, and can be used in place of the RV speed reducer.

If the connection method 2 is used to configure the speed reducer, the planetary carrier 3 supports each planetary gear using the method 1, see FIG. Similarly, connection method 2 is used, and the planetary carrier 3 supports each planetary gear using method 2, see FIG. The two ways in which the planetary carrier 3 supports each planetary gear have the same technical effect. The planet carrier 3 is connected to the input end 6, the right sun gear 2 is connected to the output end 7, the left sun gear 1 is connected to the lock end 8, and the transmission ratio of the transmission from the planet carrier 3 to the right sun gear 2 is right transmission ratio, right transmission ratio=1/(1−number of teeth of left sun gear*number of teeth of right planetary gear/(number of teeth of right sun gear*number of teeth of left planetary gear))=-220 . The transmission ratio is a negative value and the direction of rotation of the planetary carrier 3 and the direction of rotation of the right sun gear 2 are opposite.

The foregoing has described and explained the basic principles, main features and advantages of the present invention. It will be appreciated by those skilled in the art that the present invention is not limited to the foregoing embodiments, and that the foregoing embodiments and specification are merely illustrative of the principles of the invention and do not depart from the spirit or scope of the invention. Otherwise, various changes and improvements are possible in the present invention, and these changes and improvements are also included in the scope of protection of the present invention. The scope of protection sought for the invention is limited by the appended claims and their equivalents.

Claims (2)

A variable linear velocity planetary gear mechanism comprising two sun gears, an input end, an output end, a lock end,
An equal reduction gear with a variable linear speed planetary gear mechanism having two sun gears, including an auxiliary device called a bearing,
A variable linear speed planetary gear mechanism with two sun gears is composed of a left sun gear, a right sun gear, and a planetary carrier with planetary gears, the planetary carrier supporting each planetary gear and allowing each planetary gear axis to revolve. The distance to the axis, that is, the reference center distance is equal, and each planetary gear is provided with two gears, the left planetary gear and the right planetary gear, on the axis in order,
The number of teeth of the left sun gear, the number of teeth of the right sun gear, the number of teeth of the left planetary gear, and the number of teeth of the right planetary gear. The number of teeth × the number of teeth of the left planetary gear / (the number of teeth of the left sun gear × the number of teeth of the right planetary gear) is the range defining parameter, and the number of planetary gear axes supported by the planetary carrier is the number of gear sets K and
As the value range defining parameter, the value of the range defining parameter is greater than 0.875, less than 1.142857 and not 1.0 for each combination of numbers of teeth,
The gear set number K is an integer of 2 or more, and when setting the number of teeth and the number of gear sets, the rule that the combination of the number of teeth matches the number of gear sets is as follows:
(1) When the absolute value of the difference between the number of teeth of the left sun gear and the number of teeth of the right sun gear is a multiple of 2, the number of gear sets is 2;
(2) When the absolute value of the difference between the number of teeth of the left sun gear and the number of teeth of the right sun gear is a multiple of 3, the number of gear sets is 3;
(3) When the absolute value of the difference between the number of teeth of the left sun gear and the number of teeth of the right sun gear is a multiple of 4, the number of gear sets is either 4 or 2;
(4) When the absolute value of the difference between the number of teeth of the left sun gear and the number of teeth of the right sun gear is a multiple of 5, the number of gear sets is 5;
(5) when the absolute value of the difference between the number of teeth of the left sun gear and the number of teeth of the right sun gear is a multiple of 6, the number of sets of gears is 6, 3, or 2;
(6) when the absolute value of the difference between the number of teeth of the left sun gear and the number of teeth of the right sun gear is a multiple of 8, the number of gear sets is 8, 4, or 2;
(7) when the absolute value of the difference between the number of teeth of the left sun gear and the number of teeth of the right sun gear is a multiple of 10,
The number of sets of gears is either 5 or 2 ,
The manufacturing and assembling rule of the planetary gear is that the number of teeth of the left sun gear is divided by the number of gear sets K to obtain a remainder, the remainder being an integer ranging from 0 to (K-1), When manufacturing each planetary gear, for the first planetary gear, the equiphase surface is selected so that the equiphase angle value is a, and for the second planetary gear, the equiphase angle value is ( a+1 × 2π × remainder/K), and
For the third planetary gear, the equiphase surface is selected so that the equiphase angle value is (a+2 × 2π × remainder/K), and thus the fourth planetary gear, the fifth The planetary gear, the 6th planetary gear, and the 7th planetary gear are manufactured in order, and finally the equiphase angle value of the K-th planetary gear is (a + (K
-1) Select the equiphase surface to be × 2π × remainder value/K), and when assembling each planetary gear, assemble two sun gears, a planetary carrier at a predetermined position on the revolution axis, and each mounting Determine the surface, superimpose the equiphase surface with the equiphase angle value a of the first planetary gear on the first mounting surface, set the left and right equiphase points within the reference center distance, and Assemble the planetary gears, superimpose the equiphase surface of the second planetary gear whose equiphase angle value is (a + 1 × 2π × remainder value / K) on the second mounting surface, and place the left and right equiphase points within the reference center distance to assemble the second planetary gear, and superimpose the equiphase surface of the third planetary gear whose equiphase angle value is (a + 2 × 2π × remainder value / K) on the third mounting surface, Set the left and right equiphase points within the reference center distance, assemble the third planetary gear, and in this way sequentially 4th planetary gear, 5th planetary gear, 6th planetary gear, 7 Assemble the second planetary gear, etc., and finally the equiphase angle value of the Kth planetary gear is (a + (K - 1) × 2π ×
The equiphase surface that is the remainder value /K) is superimposed on the Kth mounting surface, the left and right equiphase points are set within the reference center distance, and the Kth planetary gear is assembled,
As the pitch radius of the gear, the number of teeth of the left sun gear/the number of teeth of the left planetary gear = the pitch radius of the left sun gear/the pitch radius of the left planetary gear, and the pitch radius of the left sun gear + the left The pitch circle radius of the left sun gear and the pitch circle radius of the left planetary gear are set around the reference center distance so that the pitch circle radius of the planetary gear = the reference center distance, and the number of teeth of the right sun gear/the number of teeth of the right planetary gear Right around the reference center distance such that the number of teeth = the pitch circle radius of the right sun gear/the pitch circle radius of the right planetary gear, and the pitch circle radius of the right sun gear + the pitch circle radius of the right planetary gear = the reference center distance. An equal reduction gear using a variable linear velocity planetary gear mechanism having two sun gears, characterized in that the pitch circle radius of the sun gear and the pitch circle radius of the right planetary gear are set. There are two ways to connect the three parts of the variable linear velocity planetary gear mechanism with two sun gears, the input end, the output end and the lock end. Differently, specifically:
As connection method 1, the planet carrier is connected to the input end, the left sun gear is connected to the output end, the right sun gear is connected to the lock end, and the transmission ratio of the transmission from the planet carrier to the left sun gear is the left transmission ratio , and the left transmission ratio = 1/(1 - the number of teeth of the right sun gear × the number of teeth of the left planetary gear / (the number of teeth of the left sun gear × the number of teeth of the right planetary gear)),
As connection method 2, the planet carrier is connected to the input end, the right sun gear is connected to the output end, the left sun gear is connected to the lock end, and the transmission ratio of the transmission from the planet carrier to the right sun gear is the right transmission ratio and the right transmission ratio = 1/(1-number of teeth of left sun gear x number of teeth of right planetary gear/(number of teeth of right sun gear x number of teeth of left planetary gear)) 2 the sun gear according to item 1
Equal reduction gear with variable linear speed planetary gear mechanism.

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